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Thanks for your answers. Could you explain why is it so important to exclude the bending stress component parallel to the classification line. Isn't it conservative to include all of the components? or what is the reason behind it?

I tried to verify myself, not sure how good it is (I did calculate by components first :) ) It seems to me and at least for this example that ansys is not doing that bad?http://files.engineering.com/getfile.aspx?folder=443b272a-63d7-464c-a360-2cc7d4a6db9a&file=linearization_check.xls

Actually, You wrote that the "default linearization scheme in ANSYS is not compliant", so I was hoping it could become compliant with specific settings, but maybe I misunderstood.

Could it become compliant by using “axisymmetric straight” as 2D behavior with “through thickness bending stress” ignore for the non-axisymmetric (due to bolts) 3 D model , as it is mentioned in the help : “These choices are available to any type of geometry (for example, you can choose...

I looked to ANSYS help, but it did not make it clearer especially about the "2D Behavior". I wish to "Ignore the thickness-direction bending stresses" but for that I should use "Axisymmetric Straight", which I do not clearly understand. Could you help me on that? Thanks

have a look here as well : http://www.eng-tips.com/viewthread.cfm?qid=143761

oh sorry directly way is a mistake, i mixed stuff

look at those commands : *dim to create a array parameter *vget to retrieve values and stores them in a array parameter *do (do loop ) *get to get the loc z for each node of the table *endo and then find the max or directly NSEL,S,LOC,Z,-0.2 *GET, Parameter_name , node , 0, mxloc, z...

http://books.google.com/books and write strength of material ?

I am not an expert in DM but : do you extract them with which operation ? add frozen or add material ?

With the pure penalty method, the contact force is : F=k*xpenetration k is the normal contact stiffness. A large value of k gives less penetration, but the model can oscillate and you have convergence difficulties. If the value is too small, there is too much penetration. You have too try...

have a look here : http://www.eng-tips.com/viewthread.cfm?qid=236281

to draw, use 'chart and table' : 'Selecting the Chart and Table icon button allows you to create charts of loads and/or results against time. In addition you can also chart result quantities against a load or another results quantity.' from ansys help @ : // Mechanical Application User's...

you should maybe work on the mesh? I remember having read about 'sharp angle tool' in Ansys help

Have you already tried the contact stabilization ? 'For standard contact (KEYOPT(12) = 0) or rough contact (KEYOPT(12) = 1), you can use real constants FDMN and FDMT to define contact damping scaling factors along contact normal and tangential directions. The primary goal of this contact...

We use into the Ansys command prompt, it looks something like that : coordinate_array(i,2)=NX(NodeNumberFromArray(i,1))+UX(NodeNumberFromArray(i,1))

I think the documentation you may want to look at is hidden there : // ANSYS Parametric Design Language Guide // B. GET Function Summary hope it will help

I used the command NUMMRG to "glue" two "cylinders" sections of two coincident beams and assign different materials, it works fine.

you create a line body, and RMB on "mesh" -> "method" -> "element midside nodes" : you choose "kept" to get a "beam189", "dropped" for "beam188". and to get shell element, you create a surface and mesh it?

http://www.eng-tips.com/viewthread.cfm?qid=232126 does it help ?